Web-winding apparatus and method

ABSTRACT

1. IN WEB-WINDING APPARATUS EQUIPPED WITH A FRAME, (A) A ROLL ROTATABLY SUPPORTED ON SAID FRAME, MEANS FOR ROTATING SAID ROLL, MEANS FOR FEEDING A WEB ONTO SAID ROLL FOR TRAVEL THEREWITH WHILE IN PARTIAL WRAPPING ENGAGEMENT WITH SAID ROLL, (B) SAID FRAME ALSO BEING EQUIPPED WITH A PLURALITY OF MANDRELS, MEANS FOR MOVING SAID MANDRELS SEQUENTIALLY THROUGH A PATH IN CLOSE PROXIMITY TO THE SURFACE OF SAID ROLL, THE IMPROVEMENT COMPRISING: (C) MEANS FOR TRANSVERSELY SEVERING SAID WEB TO PROVIDE A FREE LEADING EDGE ON SAID WEB FOR APPROACHING A MANDREL ON WHICH SAID WEB IS TO BE WOUND IN SAID PATH, (AND) (D) PIN MEANS EXTENSIBLY MOUNTED ON SAID ROLL FOR MAINTAINING A WEB PORTION SPACED FROM SAID EDGE IN CONTACT WITH SAID ROLL, AND PUSHER MEANS EXTENSIBLY MOUNTED ON SAID ROLL TO URGE SAID MAINTAINED WEB PORTION AGAINST AN ADJACENT MANDREL.

2 5 .A AU 4%0 BESTAVAILABLE COPY March 4, 1975 D NYSTRAND ETAL Re.28,353

WEB-WINDING APPARATUS AND METHOD 5 Sheets-Sheet 1 Uriginal Filed Sept.1'7, 1962 March 4, 1975 E. n NYSTRAND ETAL Re. 28,353

WEB-WINDING APPARATUS AND METHOD Original Filed Sept. 17, 1952 aSheets-Sheet 2 March 4, 1975 D NYSTRAND ET AL Re. 28,353

WEB-WINDING APPARATUS AND METHOD 8 Sheets-Sheet 3 Original Filed Sept.17 1962 NE QWNN MW. NW

8 mm a mwN March 4, 1975 E, 1 NYSTRAND ET'AL Re. 28,353

WEB-WINDING APPARATUS AND METHOD Original Filed Sept. 1'7, 1962 8Sheets-Sheet 4 March 4, 1975 5 D NYSTRAND ETAL Re. 28,353

WEB-WINDING APPARATUS AND METHOD Original Filed Sept. 17, 1962 8Sheets-Sheet S March 4, 1975 E. NYSTRAND ET'AL Re. 28,353

WEB-WINDING APPARATUS AND METHOD Original Filed Sept. 17, 1962 BSheets-Sheet 6 March 4, 1975 5 D NYSTRAND ETAL 28,353

WEB-WINDING APPARATUS AND METHOD Original Filed Sept. 1'7, 1962 8Sheet5-5heet 7 March 4, 1975 a NYSTRAND ET AL Re.

WEB-WINDING APPARATUS AND METHOD Original Filed Sept. 17, 1962 8Sheets-Sheet. 8

United States Patent Re. 28,353 Reissued Mar. 4, 1975 28,353 WEB-WINDINGAPPARATUS AND METHOD Ernst Daniel Nystrand, John J. Bradley, and HarveyJ.

Spencer, Green Bay, Wis., assignors to Paper Converting Machine Company,Inc., Green Bay, Wis.

Original No. 3,179,348, dated Apr. 20, 1965, Ser. No. 223,994, Sept. 17,1962. Application for reissue Sept. 1, 1972, Ser. No. 285,877

Int. Cl. B65h 19/26 US. Cl. 242-56 A 19 Claims Matter enclosed in heavybrackets I: appears in the original patent but forms no part of thisreissue specification; matter printed in italics indicates the additionsmade by reissue.

ABSTRACT OF THE DISCLOSURE An apparatus and method for rewinding aweb-sequenlially onto a plurality of core equipped mandrels is pro videdwherein the web is transversely served so as to present a folded freeleading edge which is urged into contact with a core equipped mandrel.

This invention relates to a web-winding apparatus and method and, moreparticularly, to that machine which paper converters refer to as anautomatic rewinder."

Web-winding apparatus of the character to which this invention isapplicable can be sen in Kwitek and Nystrand Patent No. 2,769,600.

Apparatus of this character is employed when a wound web must be unwoundand then rewound into smaller rolls. Illustrative of this operationinsofar as paper is concerned is toilet tissue and paper toweling. Theapparatus serves to unwind the large diameter paper rolls provided bythe paper machine and thereafter rewind the web onto cores forindividual use. The parent roll may be several feet in diameter, and itis desired to unwind this roll continuously and at a relatively highrate of speed-of the order of 2,000 feet per minute. From this, it canbe seen that the rewinding operation wherein the web is presentedultimately in the form of small, readily handleable rolls, occupies onlya few seconds.

Before the advent of the automatic rewinders, it was necessary to employstop-start rewinders where the unwinding and rewinding operation wasintermittent. The stopping was necessary in order for a new mandrel tobe placed in the path of the web being unwound. The automatic rewindersolved this problem by automatically moving the new mandrel into thepath of the web being unwound while the web was still being wound onanother mandrel.

conventionally, in the so-called automatic rewinders, the cut-oil occursat a position between adjacent mandrels. The rewinder may be equippedwith six mandrels, each of which goes through the same orbital path.This permits the mandrel to be equipped with a paperboard core on whichthe tissue or toweling is wound, the core faced with glue, the actualwinding, and ultimately the removal of the wound roll from the mandrel.Thus, near the end of rewinding on a given mandrel core, the subsequentmandrel is in a position close to the fast-traveling web so as to pickit up and continue the rewinding operation when the web has beensevered. As pointed out before, it has been the conventional practice tosever the web between the mandrel which is just finishing its rewindingoperation and the mandrel which is just to start its rewindingoperation.

To achieve transfer of the web from the one mandrel to another, it wasnecessary to synchronize the cut-off with engagement of the web with the"new" mandrelthat mandrel just about to commence the web-windingoperation. Also, the cut-off means had to be rapidly retracted so as notto interfere with the winding operation. With the advent of higher andhigher speeds-of the order of 2,000 feet per minute--it becameincreasingly more difficult to effect this necessary synchronization.Also, the more rapid retraction of the cut-off means resulted in greatershock-type stresses being applied to the rewinder, raising thepossibility of permature failure or misoperation.

Also, on multi-ply webs, only one ply is adjacent to the adhesive on thecore and the other plys were not positively transferred to the new coreby previously used mechanisms or means. This actually constituted apreviously insurmountable speed barrier of approximately 1200 f.p.m. on2-ply webs, and lower on webs of more than 2 plies.

From this, it can be appreciated that it would be desirable if thecutting of the web could be performed under conditions that lacked thecriticality characteristic of the experient just mentioned, and theprovision of method and apparatus for such cutting constitutes animportant object of this invention.

Another object is to provide a method and apparatus for rewinding websin which the severance of the web following a predetermined amount ofrewinding is accomplished under conditions where the movement of thecutting means does not have to be precisely synchronized relative to amandrel about to be wound and where the movement of the cutting membercan be adjusted so as to minimize undersirable shock to the high speedrewinding apparatus.

Still another object is to provide a method and appa rains for rewindingwebs on a series of mandrels each following the same path wherein thetransverse severance of the web is performed on that portion of the webwhich approaches the mandrel next to be wound.

Yet another object is to provide a novel method and apparatus for theart of high speed rewinding, particularly of lightweight paper webs suchas toilet tissue, toweling, etc., where the web is transversely severedat a position in its travel so as to present a free or unsupportedleading edge approaching a mandrel about to start the winding operationand wherein a portion of the web spaced from the severed edge is urgedinto contact with a core-equipped mandrel.

A further object is to provide a novel apparatus in a high speedrewinder for selectively controlling, in a predetermined fashion, theelements used to effect cut-off and transfer of the webs relative tovarious rewinding mandrels.

A still further object is to provide a positive means for transferringmulti-ply and particularly two-ply webs onto the new mandrel by trappingone ply in a fold of another ply, as by reverse folding the web. Otherobjects and advantages of the invention may be seen in the details ofconstruction and operation set down in this specification.

The invention will be explained in conjunction with an illustrativeembodiment in the accompanying drawing, in which- FIG. 1 is afragmentary side elevational view, partially in section, of an automaticrewinder employing the teachings of the invention;

FIG. 2 is an enlarged fragmentary view, partially in elevation and insection, as taken along the line 22 of FIG. 3, of the web transferportion of the apparatus (the large bedroll and the smaller chopperroll), at the time of completion of a winding cycle;

FIG. 3 is a fragmentary vertical sectional view through an end part ofthe apparatus as taken along the line 3-3 of FIG. 2;

FIG. 4 is a fragmentary sectional view of the transfer portion of theapparatus at the time a winding cycle of a single-ply web is about to beinitiated;

FIG. 5 is a fragmentary sectional view showing parts in FIG. 4 at thetime a winding cycle of a two-ply web is about to be initiated.

FIG. 6 is a view in side elevation of a portion of the chopper roll ofthe apparatus on a scale reduced from that shown in FIG. 7;

FIG. 7 is a transverse vertical sectional view through the chopper rollas taken along the line 7-7 and in a scale enlarged over that of FIG. 6;

FIG. 8 is a view in elevation of the bedroll of the apparatus as viewedfrom the open side of the bed roll and more particularly showing thebracing for the open side, the scale of FIG. 8 being considerably lessthan that of the roll appearing in FIG. 3;

FIG. 9 is a transverse vertical sectional view through the bedroll astaken along the line 99 of FIG. 8 and on the same scale;

FIG. 10 is a fragmentary perspective view of portions of the bedrollweb-transferring mechanism of the apparatus appearing in FIG. 4 but in achanged position;

FIG. 11 is a view in side elevation of one of the padcarrying membersemployed in the apparatus and the mounting therefor, on a scale enlargedover that of FIG. 4;

FIG. 12 (Sheet 3) is a vertical detail fragmentary view through aportion of the solenoid trip-actuating plunger appearing in FIG. 3 astaken along the line 12-12 of FIG. 3, with the plunger in latch-trippingposition;

FIG. 13 (Sheet 1) is a fragmentary detail view of parts of theapparatus, as viewed in the direction of the arrows l313 in FIG. 2, andwhich parts also appear on FIG. 10;

FIG. 14 (Sheet 4) is a fragmentary view in elevation of parts appearingin FIG. 2 when in a changed position;

FIG. 15 is a detailed vertical sectional view, as taken along the line15l5 of FIG. 3, and more particularly shows a certain latching mechanismemployed in the apparatus when the mechanism is in the latched position;

FIG. 6 is a view similar to FIG. 15 when the latching mechanism is inthe unlatched position;

FIGS. 17 and 18 (Sheet 6) and FIG. 19 (Sheet 2), respectively, aredetail perspective views of certain parts employed in the latchingmechanism of the apparatus; and

FIGS. 20-23 (Sheets 7 and 8) are schematic elevational views of themachine operation during the inventive sequence.

It is believed that a general description of the overall rewinder willbe helpful in understanding the particular improvements set down herein,and for that purpose the following description is given:

General description of environmental rewinder In the illustration given,and with particular reference to FIG. 1, the numeral designatesgenerally a tension control mechanism for the web W which includes adancer roll 31 positioned between idler rolls 32 supported in the pathof the web W from a parent or jumbo roll (not shown). Alternatively, theWeb W may come from a web-forming machine. Thereafter, the path oftravel of the web W carries the web past and in contact with driven pullrolls 33, a perforator roll 34, and a slitter or idler roll 35. Theperforator roll 34 advantageously may be of the type set forth in US.Patent No. 2,870,840. The rolls 33-35 are suitably iournaled in a frame31 which also carries the main cut-off bedroll 36, the bedroll 36 beingpartially wrapped also by the web W.

The numeral 38 designates generally a mandrelequipped turret which ismounted for rotation in rewinder frame 37 and which is disposed inparallel, sideby-side relation with the bedroll 36. In the illustrationgiven, the turret 3 is equipped with six mandrels 39, the

mandrels being arranged for sequential movement into web-contactingrelation.

In the operation of thhe turret 38, a core on which the web W is to bewound is inserted on the mandrel 39 in the station designated by theletter A. In the operational sequence, a mandrel 39 is rotated from thecorereceiving station A into the core-cutting station B, where aplurality of axially-spaced cutting knives or discs 40 engage the coreand cut it into predetermined lengths. Further rotation of the turret 38brings a mandrel 39 to the station designated C, and a glue-applyingmechanism 41 operates to provide each core segment with glue between thestations C and D. Still further rotation of the turret moves the mandrelinto the station D, where the new mandrel is accelerated to transferspeed preparatory to transfer. In the station D, the mandrel 39 isengaged with the driving belt 42 and is accelerated to web speed. As themandrel moves toward station E transfer occurs.

During movement from station E to station F, the mandrel 39 continuesmoving down and increasingly away from the bedroll 36. Prior to reachingstation F, a discrete, predetermined length of the web has been woundand cut off, after which the mandrel arrives in position F, which is thefinished roll-removing station.

Finished roll removal is achieved through the mechanism designatedgenerally by the numeral 43, details of which, as well as of otherstructures not pertinent to this invention, can be seen in theabove-mentioned patent. The intermittent operation of the turret 38 isachieved through a Geneva gear and other suitable mechanism (not shown),which indexes shaft 44. The mandrels 39 may be driven by the motor 45through the belt 42 previously described. For this purpose, the frame 37is equipped with a shaft 46 carrying a sheave 47 engaging the belt 42,the shaft being equipped with another sheave which engages the motorbelt 48. The motor also drives the bedroll 36 through gearing not shown.

Inventive cut-off and transfer mechanism The following constitutes abrief overall description of certain features of the invention tofacilitate understanding of the detailed description set down later inthis specification. For this purpose, reference will be had to FIGS.20-23 (drawing Sheets 7 and 8).

FIG. 21 (also FIG. 2 on Sheet 2) shows the condition of the bedroll 36and chopper roll 49 near the end of a winding cycle, while FIG. 23 (alsoFIG 4 on Sheet 4) shows the condition of these two elements at thebeginning of a subsequent winding cycle. When the bedroll 36 istravelling at 2,000 feet per minute surface speed, the FIG. 23 showingis about 0.03 second later than the showing in FIG. 21.

Referring now specifically to FIG. 20, it is seen that the web W is inthe stage of winding onto roll 50. The web W in FIG. 21 is seen in theprocess of being severed by a knife mechanism generally designated 51 soas to provide a leading edge 52 which will fold back to form a foldededge to engage the core 53 mounted on a mandrel 54 in the next windingstation. In FIG. 23 the folded edge 52a is seen in contact with the core53 under the urging of a pad 55. In FIG. 22, the pad 55 is partiallyextended from the bedroll. Thus, it will be seen that the web W issevered well in advance of the time the leading edge of the severed webis opposite the new mandrel 54, and that at the time this folded edge52a is opposite the new mandrel 54, the pad 55 urges the folded edge 52aagainst the glue-equipped core of the mandrel 54 (FIG. 23).

With the inventive construction, it is possible to utilize about 270 ofone revolution of the bedroll 36 to operate the cut-off and transfermechanismit being seen in FIG. 23 that the extension of the knifemechanism 51 does not interfere with the winding of the web W on the newmandrel 54. In the studied contrast to this, the prior art mechanismshad to achieve cut-off and transfer in the very small angular distancebetween the mandrel 54 and the wound roll 50, as seen in FIG. 21.

A further important advantage accuring from the features of theinvention just described is the unique ability to wind two-ply, ormulti-ply, tissues as seen in FIG. 5. There, the parts are in the sameoperative condition as seen in FIG. 4. but are seen operating against aweb generally designated W and made up of webs W and W". The web W" isseen to be trapped within the reverse fold provided by the leading edge52 as it is urged against the core 53 of the new" mandrel 54.

The detailed description of the illustrated embodiment can beconveniently set forth in terms of the cut-otf, which involves the knifemechanism 51 and the chopper roll 49, the transfer which involves thepads 55. and lastly the timing" which selectively provides the twofunctions of cut-off and transfer, it being appreciated that thecut-off, for example, occurs only once every 60 revolutions of the.hedroll 36 where a 600 "count toilet tissue roll 50 is being developed.Notwithstanding the fact that the winding cycle is relatively long whencompared with the time of cut-off, on an absolute basis, it is rathersmallin the specific example referred to being less than seven seconds.

Cut-off mechanism When the apparatus is in the FIG. 2 condition,transverse severing or "cut-off" of the web W is being achieved, theactual moment of severance being determined by the so-called couut"desired in the web roll 50. For different manufacturers and fordifferent types of web material, this may vary. For example, with toilettissue, the count may be 500, 650, 750, 1,000, etc. In the UnitedStates, the "count" refers to the number of squares of toilet tissuewithin the web roll, each square being 4%" on a side. The high speed ofproduction can be appreciated from the fact that a wide machine (i.e.,90" wide), can produce upwards of 200 rolls per minute.

From this, it can be seen that the cut-off must be achieved in a veryshort time, and, as pointed out previously, the prior art performed thiscut-off forwardly of the mandrel 54. Thus, there was provided a freeleading edge of the web that was forward of the mandrel 54 at the timethe mandrel 54 engaged the web W to commence its winding operation.

According to the instant invention, the cut-off is achieved prior to thetime the web W reaches the transfer zone (i.e., before the knifemechanism 51 reaches mandrel 54), and this necessarily develops a freeor unsupported leading edge on the web W when the same is approachingthe new mandrel 54.

Through the use of the pins 56 (see FIGS. 2 and 10), the leading edgesnot not fly away from the bedroll to discontinue the rewindingoperation, but develops a reverse fold configuration (see FIGS. 4 and 5which facilitates the transfer. The development of the reverse foldconfiguration can be facilitated through the employment of other urgingor maintaining means such as suction or vacuum ports.

In the illustrative embodiment, the knife mechanism (see FIG. 10)includes several axially-aligned bars or plates 57, each of which isequipped with longitudinally spaced holes (not shown) for the mountingof blades 58 and 59. The blade 58 optimally is constructed of coldroller steel thick by 1%" wide. The projecting edge portion 58a isinclined rearwardly relative to the direction of rotation and theinclined portion in the illustration given is 7-l6" wide. The plate 59is separated from the blade 58 by the plate 57 which is thick aluminum,and the blade 59 is constructed of A thick by 1 wide spring steel, theprojecting edge 59a (see FIG. 10) being equipped with 12 serrations orteeth per inch, the teeth being designated by the numeral 59b in FIG.10. and it is seen also that the trailing edge of the blade 59 is groundas at 59c and at an angle of about 60 to the plane of the blade 59.Along with the blades 58 and 59, the clip pins 56 are boltably securedto the plate 57, the pins 56 being provided as part of a U-shaped bodygenerally designated 60 (as seen in side elevation, compare FIGS. 10 and21). In the illustration given, each body 60 is l%@" wide (measuredparallel to the length of plates 57), and the pins 56 constituting onearm of the U-shape are spaced 1%" from the other arm, the pins 56tapering to a point.

The plate 57 is carried by a plurality of holders 61 which are fixed toan axially-extending shaft 62. The shaft 62 is journaled within the endsof the bedroll 36 for selective rotation so as to extend the knifeblades 58 and 59 and the pins 56 beyond the surface of the bedroll, thebedroll 36 being equipped with an opening in an opening in the surfacethereof, as can be appreciated from a consideration of FIGS. 4, 8 and 9,the open portion of the bedroll being designated 36):.

The knife mechanism 51 operates in conjunction with the chopper roll 49,which is also journaled in the frame 37 for cooperative rotation withthe bedroll 36. The roll 49, as best seen in FIG. 7, is equipped with alongitudinally-extending knife mounting slot 63, and the knife which isboltably secured within the slot is designated 64 and is seen to projectoutwardly beyond the periphery of the cylindrical surface of roll 49.The knife blade 64 is backed by a snubber 65 which advantageously can beconstructed of polyurethane foam backed with pressure-sensitive tape.Still referring to FIG. 7, it is seen that the periphery of the roll 49is relieved as at 66 for the receipt of a polyurethane foampin-impinging element 67. Alternatively, the element 67 may be combinedwith the snubber 65 as a single piece of foam adhesively secured to arelieved portion of the roll 49. The roll 49 may be equipped withrecesses 63a and 66a (see FIG. 7) to balance the roll, these recessesbeing diametrically opposed to recesses 63 and 66, respectively, andbeing somewhat smaller to compensate for the elements 64 and 67. Theelements 67 cooperate with the pins 56 in insuring proper perforation ofthe web W by the pins 56 so as to develop the reverse folded leadingedge of the web W.

In the operation of the knife blades 58, 59 and 64, it will beappreciated that the web W is impaled upon the teeth 5%, while theinclined edge 58a operates against the snubber 65 to also anchor the webW transversely across the bedroll. Thus, the chopper roll knife blade 64operates to apply a tension to the web held at longitudially spacedlines, and ruptures the same. The web is adjusted relative to the knifeblades 58, 59 and 64 so that a line of transverse perforation providedby the shear cut unit 35 lies between the blades 58 and 59. This line ofweakness, therefore, develops the line of rupture under the pressureimposed by the chopper roll blade 64.

Transfer mechanism The pads 55, as best seen in FIG. 10, operatesbetween the projecting fingers or pins 56 and are mounted on holders 68(see FIG. 11). Each pad 55, as illustrated, is a 46" wide by 84" thickpolyurethane foam piece, folded on the end of and adhesively secured tothe arm 68a. The holders 68 are advantageously constructed of 4:" x 56"aluminum and are angularly deformed as at 68a. One leg of the holder 68is secured against a clamp member 69 by means of a U-bolt 70 suitablyequipped with nuts 71. The U-bolt 70 extends around a rocker shaft 72,which is journaled in the bedroll in the same fashion as the rockershaft 62 for the knife mechanism 51. In similar fashion, the pads 55 areprojeetable or extensible out of the openings 36a in the surface of thebedroll 36, the bedroll 36 being suitably braced as at 36b across theopening 36:: (see FIGS. 8 and 9).

As can be appreciated from a consideration of FIG. 13, the openings 36aare partially covered by means of cover plates 62a and 62b. Thecoverplate 62a overlies the portion of the openings 36a radially alignedwith the knife shaft 62, while the coverplate 62b overlies the pusherpad shaft 82, these shafts being suitably rotatably supported in bearingblocks 72b and 82b supported on the cross braces 36b, as seen in FIGS.13 and 9. Each transfer pad 55 is associated with an opening 82cprovided in the coverplate 72a (see FIG. 13), while the spacing for thetwo coverplates 62a and 72a provide an elongated slot S through whichthe knife blades 58 and 59 issue.

At the time of transfer, as seen in FIGS. 4 and 5, the pad 55 projectsout of the bedroll opening 63 to urge the reversely folded web againstthe mandrel 54 so as to initiate a new winding cycle.

Timing mechanism The mechanism for extending and retracting the knifemechanism 51 and the pressure pads 55 includes a camming system,selectively energized at the end of a given and 16 (Sheet 6), and hencereference will be made to those views.

In each view, it is seen that again the rocker shafts are designated 62and 72, respectively, for the knife mechanism and the transfer pads, therocker shaft 72 also being seen in FIG. 3 where it is journaled in thebedroll head 73 in needle bearings 73a. First, however, with respect tothe rocker shaft 62, it is seen that the shaft is equipped with a springarm 74. The arm 74 is rigidly clamped about the rocker shaft 62 by meansof a bolt 75. The spring arm 74 is equipped with post 76 which providesa mounting for a coiled spring 77 which, at its other end, is mounted ona post 78 provided as part of the inside of the bedroll end head 73.Thus, the spring 77 tends to pivot the spring arm 74 in acounterclockwise fashion about the axis of shaft 62, except for theholding action of the latching mechanism, which will now be described.

For the purpose of latching the spring arm 74 in the FIG. 15configuration, the latching mechanism includes a trip latch member 80which bears against a cam follower 79 mounted is spring arm 74 (see FIG.15). The trip latch member 80 is rigidly clamped on a cam latch shaft 81by means of a block portion 80a. Unlike the rocker arms 62 and 72, thecam latch shaft is relatively short, being journaled in the bedroll.endhead 73 in a fashion analogous to the cam latch shaft 82 as seen in FIG.3 and associated with the transfer pad mechanism. In FIG. 3, the shaft82 is mounted in needle bearings 73b provided in the header 73 of thebedroll 36. Here, it will be appreciated that FIG. 3 reflects only aportion of the timing mechanism, primarily that associated with thetransfer pad mechanism seen on the left-hand side of FIG. 2. However,the latching and camming mechanism for the knife mechanism 51 is similarto the camming and latching mechanism for the transfer pads 55.

Referring again to FIGS. 15 and 16, it will be seen that the trip latchmember 80 is urged out of engagement with the cam follower 79 by meansof a spring 83. For this purpose, the spring 83 is secured at one end toa post 80b provided as part of the trip latch member 80, and at theother end to a post 84 provided on an arm portion 85 which is integralwith the trip cam housing collar 86. The collar 86 is seen inperspective in FIG. 17 and is fixed relative to the frame 37 so that theshaft 81 can rotate relative thereto (compare FIGS. 15 and 16). Thecollar 86 is equipped with a second arm or projection 87 carrying ascrew 88 which serves to limit the return of the trip latch 80 to itslatched position as seen in FIG. 15.

The remaining structure associated with the cam latch shaft 81 can beseen in FIGS. 14 and l9. There, it is seen that a trip cam 89 is fixedto a trip cam arm 90, which in turn is secured to the shaft 81. The tripcam arm 90 carries a cam follower roller 91 which, when the shaft 81rotates to the FIG. 16 condition, follows the contour of the inside camsurface 92a of cam 92 (see FIG. 2).

When the shaft 81 is in the FIG. 16 condition, the shaft 62 is likewisein its FIG. 16 condition by virtue of the action of the spring 77 so asto position the cam follower 93 in contact with the exterior cam surface92b (see FIGS. 2 and 14). The cam member 92 (see FIG. 3) is secured tothe frame 37 by bolts extending through bolt holes 92c. The cam follower93 is carried by a cam follower arm 94 rigidly fixed to the shaft 62.

Before describing the operation of the cut-off timing cams, etc., adetailed description of the transfer camming mechanism will be given,along with the means for actuating both sets of camming mechanisms.

Referring first to FIG. 15, it will be seen that the numeral 82designates the cam latch shaft (being the counterpart of shaft 81 forthe cut-off mechanism). The shaft 82 has fixed thereto a trip latchblock 95a providing trip latch arm 95 (see FIG. 18) equipped with aprojecting arm portion 96 which performs the same function in thetransfer mechanism that the trip latch 80 does in the cutoff mechanism.The arm 96 is equipped with a laterallyextending post 97 which securesone end of a spring 98, the other end of which is fixed to a post 99carried by an arm 100 provided as part of a trip cam housing collar 101.The housing 101 is similar to the housing 86 seen in FIG. 17 and carriesa second arm projection 102 in which is threadedly received a stop screw103.

The shaft 72 which carries the transfer pads 55 and the arms 68 thereforis equipped with a spring arm 104, the arm 104, and hence the shaft 72,being urged in a clockwise fashion by means of a spring 105. The spring105, at its other end, is secured to a post 106 analogous to the fashionof securement of the spring 77 (see also FIG. 15).

Additionally, as can be seen in FIG. 14, the shaft 72 carries a camfollower arm 107 rotatably supporting a cam follower 108. The camfollower 108, like the cam follower 93, rides against a cam surfaceprovided fixed on the frame 37.

Completing the elements in the camming mechanism for the transferportion of the apparatus, the numeral 109 designates a trip cam which isfixed to the shaft 82 and which is supported on a trip cam arm 110(still referring to FIG 14) and which carries a cam follower 111. Also,as in the case of the cut-otf mechanism, a cam follower is provided onthe spring arm. In the case of the transfer mechanism, the cam followeris designated 112 and is rotatably mounted on the spring arm 104.

Turning now to FIG. 3 (Sheet 3), a transverse section of the machinethrough the transfer camming mechanism is seen. The numeral 37 againdesignates the main frame of the machine, and seen bolted to the frameas at 113 is a bracket 114. The bracket 114 in turn supports a bearinghousing 115, so that the housing 115 is spaced between the inside of theframe 37 and the header 73 of the bedroll 36. The housing 115 carriesthe cam 92 which provides the outer contour 92b (see FIG. 2) forengagement by the cam followers 93 and 108, the cam 92 providing aninner surface 92a engageable by the cam followers 91 and 111.

Also supported on the frame 37 is a solenoid 116 (see FIG. 3), which isseen in its two conditions in FIGS. 3 and 12. In FIG. 3, the solenoid ispositioned so as not to actuate the trip cams 89 and 109, while in FIG12 the position for tripping the two cams 89 and 109 is seen. Referringto FIG. 12, the solenoid is seen to be equipped with an armature 117which operates against a cap 118. Interposed between the shoulder 118aof the cap 118 and the bearing housing 115 is a coiled spring 119. Thecap 118 carries a cam follower shaft 120. At its extended end, the shaft120 carries a cam follower 121 which in FIG. 12 is seen to be inengagement with the trip cam 109. The trip cam 109 is also seen in FIG.3 and is seen to be fixed to cam latch shaft 82, which is iournaled inthe trip cam shaft housing bracket 122 bolted to the bedroll header 73.As seen in FIG. 14, the numeral 110 designates the trip cam arm alsoseen in FIG. 3, and the numeral 101 designates the trip cam housingcollar which is fixed to the bracket 122. The collar 101 is equippedwith the post 100 and the spring 98 connecting the post 100 as at 99with the pin 97 provided on the latch trip 95 is also seen. The springarm 104 in FIG. 4 is seen to be mounted on the shaft 72, and this isbiased by means of spring 105 which is connected to the header by meansof pin 106.

Operation of timing mechanism In the operation of the camming mechanismjust described, the sequence is started by energization of the solenoid116. this occurs when the bedroll blades 58 and 59 are opposite thechopper roll blade 64, and one revolution of the bedroll 36 prior to thedesired cut-off. This can be conveniently achieved through a countingmechanism (not shown) synchronized with the drive gear 123 (see FIG. 3)which is provided as part of the bedroll 36.

Upon energization of solenoid 116, the armature 117 moves to the FIG. 12position and the cam follower 121 is thereby aligned with the trip earns89 and 109 associated with the cut-off and transfer mechanisms,respectively (see particularly FIG. 14). As the bedroll continues torotate, the trip cams 89 and 109, in that order, strike the cam follower121. The trip earns 89 and 109 are thus moved in a clockwise fashionfrom the FIG. 14 configuration to the FIG. 2 condition, turning theshafts 81 and 82 correspondingly. This results in the cam followers 91and 111 riding on the inner surface 92a of the cam 92.

The clockwise movement of the shafts 81 and 82 necessarily disengagesthe trip latches 80 and 95 from the cam followers 79 and 112,respectively, converting the apparatus from the FIG 15 showing to theFIG. 16 showing. In this connection, it will be noted that FIGS. 15 and16 are opposite hand to the showing in FIGS. 2 and 14. It is seen thatthe end 124 of the arm 96 (and also the arm of latch 80) is peaked (FIG.18) to provide an over-center latching action, the follower 112, forexample, bearing against the surface 124a during the latched position.

As the trip latches 80 and 95 are moved, the spring arms 74 and 104 and,therefore, the shafts 62 and 72, respectively, are rotated under theurging of springs 77 and 105. For this purpose, compare the positions ofspring arms 74 and 104 in FIGS. 15 and 16. This movement results in thecam followers 93 and 108 being pivoted into contact with the exteriorsurface 92b of cam 92.

At this juncture, the apparatus is prepared for cut-off and transfer.After these two operations have been performed, relatching of the twomechanisms is in order for the ensuing winding cycle. This occursthrough the vehicle of the cam followers 91 and 111 following thecontour 92a of the cam 92, which is equipped with a latching surface 92dterminating in a step 92e (see FIG. 2).

Referring to FIG. 2 in particular, the numeral 115 (applied at the lowerright) indicates the outline of the frame member supporting the cam 92away from the main frame 37 and close to the bedroll 36, and it is seenthat the cam surfaces 92a and 92b are concentric to the bedroll axis,with the cam maximum rise being at the bottom of the view. The portion92d of the inner cam surface 92a is increasingly spaced from the housingperiphery (the dotted line designated 115) until the drop-off point 92cis reached. When the cam follower 91, for example, engages the portion92d, it is caused to move inwardly,

i.e., toward the center of the bedroll 36. At this stage, the camassembly, particularly the shaft 81, is in the condition seen in FIG.16. Again, it should be understood that FIGS. 15 and 16 are views takenin opposite directions from FIGS. 2 and 14, for example. In FIGS. 2 and14, the viewer is looking into the bedroll from the outside, while inFIGS. 15 and 16 the view is from the inside of the bedroll lookingaxially outwardly. Thus, the movement of the cam follower 91 inwardlyresults in a counterclockwise rotation of the shaft 81 in FIG. 2 or FIG.14, but a clockwise rotation in FIG. 16. As the peak point 92c of thecam is reached, the trip latch arm is positioned as seen in FIG. 15 andengaged with the cam follower 79 associated with the knife mechanismshaft 62. Meanwhile, the cam follower 93 has been fol lowing the surface92b and has pivoted the shaft 62 to position the cam follower 79 forengagement with the face 80c of the peaked arm 80 (see FIG. 15). Thisengagement lifts cam follower 91 so as to space follower 91 from the camsurface 92a during the latched condition, i.e., the configuration seenin FIGS. 14 and 15.

Precisely the same operation is followed relative to the cam follower111 associated with the rocker shaft 82 so as to latch the shaft 72(associated with the transfer pads) into a retracted condition.

Still referring to FIG. 2, and comparing the same with FIG. 23, it willbe seen that the arcuate distance between the point of trip of the tripcam 109 by the solenoid 116 to the point of maximum projection is about135. When this happens (i.e. tripping), the cam follower 108 falls amatter of about 0.00 i.e. moves inwardly, and then gradually movesfurther inwardly over the 135 arc to extend the transfer pads associatedtherewith. The same action has previously occurred relative to the knifemechanism 51. The cam and trip arrangement presented here means thatcentrifugal force has little or no effect upon the operation of thelatching and unlatching mechanism so that high speeds are possible whilestill being characterized by smooth gradual action of the knifemechanism 51 and the transfer pads 55.

From the foregoing, it will be seen that neither cam follower 93 nor 108(which determine the operation of the cut-0E knives 58, 59 and thetransfer pads 55, respectively) engages the cam surface 92b when thewinding cycle is at any stage but in the final revolution of the bedroll36. Also, the setscrews 88 and 103 are so adjusted as to prevent thetrip latches 80 and from travelling too far over center when themechanism is latched. Otherwise, there would be contact of followers 93and 108 with surface 92b. Further, the machine is so arranged that thebedroll knives 58 and 59 clear the core 53 and the mandrel 54 by about14 when the mechanism is unlatched, i.e. in the FIG. 2 condition.

Summary of operation When the bedroll blades 58 and 59 are opposite thechopper roll blade 64, one revolution of the bedroll 36 prior to thedesired cut-off, the solenoid 116 is energized. Thereupon, the solenoidcam follower 121 is moved into extended position to trip the latches 89and 109 (see FIG. 2). The latch 89 strikes cam follower 121 and rotatesshaft 81, thereby moving latch 80 (see FIG. 15) out of engagement withcam follower 79. Thereupon, cam follower 91 (see FIG. 2) rests upon theinner surface 92a of cam 92.

Simultaneously with this, the spring 77 pivots the shaft 62 until thecam follower 93 rests upon the outer surface 92b of the cam 92.

Trip cam 109 of the transfer mechanism thereafter strikes the solenoidcam follower 121 to rotate the shaft 82 so as to move the trip latch 95out of engagement with cam follower 112. Thereupon, the cam follower 111contacts the inner surface 92a of the cam 92. The cam follower 108 isbrought into engagement with the outer sur- 1 1 face 92b of the cam 92by virtue of the spring 105 pivoting the shaft 72.

At cut-off, the foam web snubber 65 holds the web W firmly against thecut-E blade 58. The chopper roll blades 64 passes between the bedrollblades 58 and 59, severing the web W at the transverse line ofperforation provided by the perforator 34. The element 67 presses thesevered web firmly onto the pins 56 of the body 60, and these pins 56carry the severed web to the transfer point. At cut-off, however, asseen in FIG. 21, the pins 56 are already piercing the web before the webis actually severed.

Before transfer, the machine windage (air current) folds the severed webback over the pins 56 and the transfer pads 55 press the web firmlyagainst glue strips on the core 53 and the mandrel 54.

Thereafter, the cam follower 91 follows the inner surface 92a of the cam92 until it engages the relatch surface portion 92d, whereupon itgradually causes shaft 81 to rotate, moving trip latch 80 intoengagement with cam follower 79, lifting cam follower 93 out ofengagement with surface 92b. In like fashion, the cam follower 111follows the inner surface 92a of the cam 92, rotating shaft 82 andmoving trip latch 95 into engagement with cam follower 112, lifting camfollower 108 free of the surface 92b.

The cut-off, transfer, and actuating mechanisms just described areeffective for both two-ply and singly plytissue and at speeds ofrewinder operation in excess of 2,000 feet per minute. During thisoperation and with the cut-off knife mechanism 51 being actuated whilethe web W is in partial wrapping engagement with the bedroll 36 (i.e.,ahead of the mandrel 54), the leading edge has been found to extendfirst radially relative to the bedroll, and thereafter, presumably underthe combined stresses of centrifugal force and air resistance, foldedback somewhat tangentially to develop the reverse fold conditiondepicted in FIG. 4.

Irrespective of the means employed to urge the fold against the bedroll,a cut-off is provided ahead of the mandrel 54 with the knife mechanism51 issuing relatively slowly (compared with prior art operations) andalso returning slowly, so that there is a significant reduction in shockto the bedroll and associated components to facilitate the achievementof maintenance-free operation of the rewinder at the high speedsindicated. Thereafter, each pad 55 issues again relatively slowly tourge the folded edge of the sheet onto the glued core with which themandrel 54 is equipped.

It will be seen that there is provided an entirely new concept of webconfiguration during transfer. According to the invention, the side ofthe web next to the bedroll 36 is glued to the core. This means that theinvention handles multi-ply webs as easily and consistently assingle-ply webs. The invention also makes it possible to sever the webahead of the mandrel 54 rather than right after the mandrel, aspreviously followed. This improvement provides the time to operate acut-off mechanism at very high machine speeds with reasonable loads onthe various parts. Thus, the web cut-off system which is extremelyreliable may sever the web even if the web is not transverselyperforated. In the particular illustration given, the chopper roll 49and bedroll 36 are driven in precise synchronization, as by a gear train(not shown), making possible the reliable cut-off.

Also advantageous in the use of the invention are the pins 56 to holdthe severed web W on the bedroll. The temporary maintenance of the webin place is overcome by pushing means made up of pads constructedadvantageously of polyurethane foam extending between the two-tinedunits of the pins 56-a pair of pins" 56 being aligned with each gluestripe on the core so that the pad 55 therebetween will be effective inadhcsively uniting the web W to the core 53. It will also be noted thatthe cut-off knife mechanism 51 is a separately-operated memher from thetransfer pads 55 Thus, there is separate control of each operation,permitting best performance of each action independent of the other.

In the illustration given, the motion of the knife mechanism 51 and pins56 and the transfer pads 55 occupies 270 of rotation of the bedroll 36,which makes the cutoff and transfer action very gentle and thereforesuitable for high speed operation--in excess of 2,200 feet per minute.The followers 93 and 108 are apart which causes transfer to lag cut-offby the same arcuate amount, thus eliminating use of two separate camsfor the two operations-and permitting the wind effect to occur. Duringthe remainder of the cycle of winding, the transfer elements aresecurely latched away from an operational condition While, in theforegoing specification, a detailed description of an embodiment of theinvention has been set down for the purpose of illustration thereof,many variations in the details herein given may be made by those skilledin the art without departing from the spirit and scope of the invention.

We claim:

1. In web-winding apparatus equipped with a frame,

(A) a roll rotatably supported on said frame, means for rotating saidroll, means for feeding a web onto said roll for travel therewith whilein partial wrapping engagement with said roll,

(B) said frame also being equipped with a plurality of mandrels, meansfor moving said mandrels sequentially through a path in close proximityto the surface of said roll, the improvement comprising:

(C) means for transversely severing said web to provide a free leadingedge on said web for approaching a mandrel on which said web is to bewound in said path, [and] (D) pin means extensibly mounted on said rollfor maintaining a web portion spaced from said edge in contact with saidroll, and pusher means exrensibly mounted on said roll to urge saidmaintained web portion against an adjacent mandrel.

2. In web-winding apparatus having a frame,

(A) a roll rotatably supported on said frame,

(1) means for rotating said roll,

(2) means for feeding a web onto said roll for travel therewith while inpartial wrapping engagement with said roll,

(3) a longitudinal-extending recess in the surface of said roll,

(4) a cutting knife in said recess mounted for extension therefrom intocutting engagement with said web,

(B) a plurality of mandrels mounted on said frame,

(C) means for moving said mandrels sequentially through a segmental pathin close proximity to the surface of said roll, and

(D) means for extending said knife at a time during the rotating of saidroll to provide a folded free leading edge on said web during the webapproach to a mandrel on which said web is to be wound in said pathsegment, and means for maintaining a web portion spaced from said edgein contact with said roll, said roll being equipped with web pushermeans spaced rearwardly in the direction of web travel from said knife,and means for extending said pusher means at a time during the rotationof said roll when said pusher means is positioned adjacent said pathsegment.

[3. The apparatus of claim 2 in which said roll is equipped with webpusher means spaced rearwardly in the direction of web travel from saidknife, and means for extending said pusher means at a time during therotation of said roll when said pusher means is positioned adjacent saidpath segment] 4. In web-winding apparatus having a frame,

(A) a roll rotatably supported on said frame,

(1) means for rotating said roll,

(2) means for feeding a web onto said roll for travel therewith while inpartial wrapping engagement with said roll,

(3) the roll having a longitudinally-extending slot in the surfacethereof, said roll carrying a knife extendable out of said slot forcutting engagement with said web,

(B) turret means rotatably supported on said frame,

(1) a plurality of mandrel mounted on said turret means, means forrotating said turret means to move said mandrels sequentially through anorbital path,

(2) said turret means being positioned on said frame relative to saidroll to provide a segment of said orbital path in close proximity to thesurface of said roll,

(C) means on said frame for maintaining a severed web against saidsurface,

(D) a pusher mounted in said roll for extension out of said slot toovercome said maintaining means, said pusher being mounted rearwardly ofsaid knife in the direction of roll rotation, and means for sequentiallyextending said knife and pusher, said extending means being operative toextend said pusher at a time when said slot is aligned with said pathsegment.

5. The apparatus of claim 4 in which said extending means comprises camfollowers for the extending of said knife. and pusher only during onepredetermined roll revolution out of a plurality of revolutionsconstituting a winding cycle, said extending means further comprisingmeans for positively locking said cam means during the remainder of saidwinding cycle.

6. In a rewinder having a frame,

(A) a bedroll mounted for rotation in said frame,

(1) means for rotating said bedroll,

(2) means for feeding a web to said bedroll for travel therewith and inpartial wrapping engagement therewith,

(B) a plurality of elongated mandrels mounted on said frame disposedparallel to the length of said bedroll,

(1) means for selectively rotating said mandrels,

(2) means for moving said mandrels in a path having a path portionadjacent said bedroll whereby said web is adapted to be secured on amandrel in said path portion, and

(C) means for severing said web transversely to its direction of traveland at a position in the web travel prior to said path portion wherebysaid web presents a folded free leading edge in approaching acore-equipped mandrel in said path, said means including alongitudinally-extending slot in the surface of said bedroll, a cuttingknife extensibly mounted in said slot, pin means extensibly mounted insaid bedroll slot rearwardly in the direction of web travel from saidknife, pusher means extensibly mounted in said bedroll slot, means insaid bedroll for extending said knife, pin means and pusher means, and achopper roll mounted for rotation on said frame, said chopper roll beingequipped with longitudinally-extending, circumferentially spaced-apart,resilient pads for coaction with said knife and pin means, whereby saidknife, pads and pin means coact to urge said web rearward of said freeleading edge into contact with said bedroll for subsequent transfer bysaid pusher means.

7. In a rewinder having a frame,

(A) a bedroll mounted for rotation in said frame,

(1) means for rotating said bedroll,

(2) means for feeding a web to said bedroll for travel therewith and inpartial wrapping engagement therewith,

14 said frame disposed parallel to the length of said bedroll,

(1) means for selectively rotating said mandrels,

(2) means for moving said mandrels in a path having a path portionadjacent said bedroll whereby said web is adapted to be secured on amandrel in said path portion,

(C) a knife extendably mounted in said bedroll, pin means on said knifespaced rearwardly thereof in the direction of web travel,

(D) means for extending said knife during the time said knife isapproaching said path portion,

(E) a chopper roll journaled in said frame for cooperative rotation withsaid web-wrapped bedroll, means on said chopper roll for urging said webporagainst said pin means,

(F) pusher means extendably mounted on said bedroll longitudinallyaligned with said pin means, and

(G) means for extending said pusher means at a time when said pushermeans is aligned with said path segment and during the same rotation ofsaid webwrapped bedroll in which said knife is extended.

8. The rewinder of claim 7 in which said pusher means includes an armmember positioned between pins constituting said pin means, and aresilient pad on said arm aligned with said pins.

9. The rewinder of claim 7 in which said pad is constructed ofpolyurethane foam.

10. The rewinder of claim 7 in which said means for extending saidpusher means is equipped with means for retracting said pusher means,said knife-extending means and pusher means-retracting means beingarranged to provide an elapsed time between initiation of knifeextension and completion of pusher means retraction of from about $6 toof one revolution of said web- Wrapped bedroll.

11. In a rewinder having a frame,

(A) a bedroll mounted for rotation in said frame,

(1) means for rotating said bedroll,

(2) means for feeding a web to said bedroll for travel therewith and inpartial wrapping engagement therewith,

(B) a plurality of elongated mandrels mounted on said frame disposedparallel to the length of said bedroll,

(1) means for selectively rotating said mandrels,

(2) means for moving said mandrels in a path having a path portionadjacent said bedroll whereby said web is adapted to be secured on amandrel in said path portion,

(C) knife means extensibly mounted in said bedroll,

(1) said knife means including a pair of circumferentially spaoed-apart,longitudinally-extending blades,

(2) said knife means including means for maintaining said web in contactwith said bedroll, said maintaining means being spaced rearwardly ofboth of said knife blades in the direction of bedroll travel,

(D) means for extending said knife blades during the time said knifeblades are approaching said path p (E) a chopper roll journaled in saidframe for cooperative rotation with said web-wrapped bedroll, a knifeelement in said chopper roll for cooperative action with said knifeblades in said bedroll,

(F) pusher means extensibly mounted in said bedroll and spacedrearwardly of said knife blades for overcoming said maintaining means,and

(G) means for extending said pusher means at a time when said pushermeans is aligned with said path segment.

12. The rewinder of claim 11 in which said frame is equipped with a camhaving interior and exterior sur- (B) a pluarilty of elongated mandrelsmounted on faces, said knife blade-extending means and said pushermeans-extending means each including a cam follower for engagement withsaid exterior cam surface, a latching cam follower for each exteriorsurface cam follower, said latching cam followers being mounted forengagement with said interior cam surface, and electro-mechanical meansfor selectively engaging said cam followers with said interior andexterior cam surfaces.

13. In a method of rewinding webs, the steps of advancing a web insynchronism with a supporting roll, transversely severing said web toprovide a folded free leading edge, and positioning a core-equippedmandrel in the path of the leading edge of said web, said web,rearwardly of said leading edge, being maintained against saidsupporting roll and thereafter urged outwardly from said roll againstsaid mandrel.

14. In a method of winding a portion of a moving web upon a rotatingcore having adhesive areas on its periphery to form a roll thereon, thesteps of (A) folding the advancing margin of said web back upon itselfwhile in movement, and

(B) exerting a force against that part of the web underlying said marginto press the same in an adhering union with the periphery of said coreto initiate the winding of a roll thereon.

15. The method of claim 14 in which said web is a multi-ply web.

16. In a method of rewinding a lightweight paper tissue web at speeds ofthe order of 2,000 feet per minute, the steps of partially wrapping saidweb about a cut-off roll, positioning two mandrels adjacent said rollwith each mandrel being operative to move through the same path, windingthe web issuing from said roll about the mandrel forward in said path,when said forward mandrel has been wound to a predetermined extenttransversely severing said web in the portion thereof wrapped on saidroll whereby a free leading edge is provided on said web to approach theother of said mandrels, maintaining a portion of said web rearward ofsaid leading edge against said roll to cause the web portion betweensaid leading edge and said rearward portion to assume a reverse foldconfiguration, whereby a double web thickness is interposed between saidother mandrel and roll, and urging said double web thickness againstsaid other mandrel.

17. The method of claim 16 in which said web is a multi-ply web wherebythe ply thereof in contact with said roll is also urged against saidother mandrel.

18. In web-winding apparatus having a frame, a roll rotatably supportedon said frame, means for rotating said roll, means for feeding a webonto said roll for travel therewith while in partial wrapping engagementwith said roll, a longitudinally-extending recess in the surface of saidroll, a cutting knife in said recess mounted for extension therefrominto cutting engagement with said web, a plurality of mandrels mountedon said frame, means for moving said mandrels sequentially through asegmental path in close proximity to the surface of said roll, means forextending said knife at a time. during the rotating of said roll toprovide a free leading edge on said web during the web approach to amandrel on which said web is to be wound in said path segment, said rollbeing equipped with web pusher means spaced rearwardly in the directionof web travel from said knife, means for extetnding said pusher means ata time during the rotation of said roll when said pusher means ispositioned adjacent said path segment, the means for sequentiallyextending said knife and pusher means including a cam follower for eachof said knife and pusher means, cam means for said cam followersoperative to sequentially move said cam followers at a predeterminedtime in a predetermined revolution of a rewinding cycle, and means formaintaining said cam followers out of contact with said cam means exceptduring said predetermined revolution.

19. The apparatus of claim 18 in which said means for maintaining saidcam followers out of contact and said cam means include latching meanspivotally mounted on said roll, and solenoid means on said frame forunlatching said latching means.

20. In web-winding apparatus having a frame, a roll rotatably supportedon said frame, means for rotating said roll, means for feeding a webonto saidroll for travel therewith while in partial wrapping engagementwith said roll, a longitudinally-extending recess in the surface of saidroll, a cutting knife in said recess mounted for extension therefrominto cutting engagement with said web, a plurality of mandrels mountedon said frame, means for moving said mandrels sequentially through asegmental path in close proximity to the surface of said roll, means forextending said knife at a time during the rotating of said roll toprovide a free leading edge on said web during the web approach to amandrel on which said web is to be wound in said path segment, said rollbeing equipped with circumferentially spaced-apart knives, and a chopperroll rotatably mounted on said frame carrying a blade insertable betweensaid spacedapart knives.

References Cited The following references, cited by the Examiner, are ofrecord in the patented file of this patent or the original patent.

UNITED STATES PATENTS 2,200,905 5/1940 Wood 24256 R 2,237,759 4/1941Kwitek 242-56 R 2,512,900 6/1950 Kwitek 24256.6 2,585,226 2/1952Christman 242-56.6 2,950,873 8/1960 Nelson 24256 A 3,128,057 4/1964Barnhart et a1 242-56 R FOREIGN PATENTS 587,197 11/1959 Canada 24256 AGEORGE F. MAUTZ, Primary Examiner

